Solenoid operated fluid control valve

ABSTRACT

Solenoid operated fluid control valve for controlling the pressure of a fluid in a fluid control system comprises a solenoid housing having therein a solenoid coil, an armature movable in response to electrical current applied to the solenoid coil, a valve member for controlling fluid flow to a fluid passage, an actuator pin disposed between the armature and the valve member for moving the valve member in response to armature movement, and one or more features including an armature damping member, tubular actuator pin support body, flow diverter, coil bobbin support sleeve, and/or internal particle gettering magnet to improve valve operation.

FIELD OF THE INVENTION

The present invention relates to a solenoid operated fluid control valvethat controls fluid pressure in a fluid system in response to electricalcurrent applied to a valve solenoid.

BACKGROUND OF THE INVENTION

A proportional variable force solenoid control valve that is relativelow in cost to manufacture and compact in size while maintainingsubstantially linear proportional fluid control is described in theNajmolhoda U.S. Pat. No. 4,988,074. The patented proportional variableforce solenoid control valve comprises an outer steel solenoid housingand an aluminum valve member housing joined together mechanically suchas by tabs on the steel solenoid housing being crimped about regions ofthe aluminum valve member housing.

The proportional variable force control valve includes a ferromagnetic(e.g. steel) armature suspended by low spring rate springs at oppositeends of the armature within the bore hole of a coreless solenoid bobbinfor reciprocable movement between positions corresponding to a closedvalve position and fully open valve position in response to appliedelectrical current to an electromagnetic coil. The position of thearmature is controlled by balancing the variable force of anelectromagnetic field of an electromagnetic coil and the force of themagnetic field of a permanent ring magnet against the force of acompression coil spring which biases the valve toward the closedposition of the valve. The electromagnetic coil, bobbin and armaturereside in the steel solenoid housing in a manner that the steel housingprovides a concentration of flux of the electromagnetic field at thearmature. The fluid control valve on the end of the armature movesrelative to a valve seat disposed in the aluminum valve housing tocommunicate a fluid inlet to fluid exhaust ports so as to regulate fluidpressure at fluid control ports in a manner proportional to themagnitude of applied electrical current.

A commercially manufactured version of the aforementioned patentedproportional variable force solenoid fluid control valve has beenmodified to include a stainless steel ball valve and a separatestainless steel valve seat insert pressed in the nozzle. The ball valveis captured in a stainless steel cage between the valve seat and arod-like, cylindrical shaped steel armature that moves relative to thevalve seat in a manner proportional to the magnitude of electricalcurrent applied to the electromagnetic coil. As the armature movesrelative to the valve seat to actuate the valve, the ball valve iscaused to follow the end of the armature by virtue of fluid pressure inthe valve member housing and confinement in the ball valve cage in thebobbin. The fluid inlet is communicated to fluid exhaust ports byopening of the ball valve so as to regulate fluid pressure at fluidcontrol ports in a manner proportional to the magnitude of electricalcurrent applied to the coil.

A spool valve is disposed in the valve member housing for providing atwo stage, high flow capability wherein pressurized fluid supplied tothe inlet port initially is directed to bypass the control ports andflows to an end of the spool valve to move it from a zero fluid flowspool position to a maximum fluid flow spool position relative to thecontrol ports as determined by the cracking pressure preset for the ballvalve by adjustment of the coil spring force. Thereafter, a second stageof operation involves controlling the fluid flow through the controlports by moving the spool valve between minimum and maximum flow spoolpositions in a manner proportional to the magnitude of electricalcurrent to the coil. Such proportional variable force solenoid controlvalves commercially manufactured to-date are operably mounted to a castaluminum transmission body or case by a clamp plate, bolt, or bothengaging an outer nozzle groove.

The Najmolhoda U.S. Pat. No. 5,611,370 describes a proportional variableforce solenoid control valve that includes a substantially non-magneticcommon housing for the solenoid and control valve, simplifying valvemanufacture and construction while maintaining substantially linearproportional fluid pressure control.

The Najmolhoda U.S. Pat. No. 5,984,259 also describes a proportionalvariable force solenoid control valve that includes a damping memberconnected to or part of the armature to provide improved valve responsestability to noise in the controlled fluid system, especially in use inan electronically controlled hydraulic automatic transmissionapplication.

Mullaly U.S. Pat. No. 5,711,344 describes a hydraulic pressureregulating valve having a dual ball and pin arrangement operativelyassociated with the armature.

SUMMARY OF THE INVENTION

The present invention provides a solenoid operated fluid control valvefor controlling the pressure of a fluid in a fluid control systemwherein the fluid control valve includes features to improve valveoperation.

Pursuant to an embodiment of the invention, the solenoid fluid controlvalve includes a solenoid coil, an armature movable in response toelectrical current applied to the solenoid coil, a valve member forcontrolling fluid flow to a fluid passage, an actuator pin disposedbetween the armature and the valve member for moving the valve member inresponse to armature movement, and further features that a dampingmember is associated with the armature proximate an end thereof so as tomove therewith and is received in a fluid-containing damping chamberformed by a tubular actuator pin support body in a fluid-containinghousing of the fluid control valve. The actuator pin support bodyincludes in one embodiment a first tubular sleeve section disposed aboutthe damping member for forming the damping chamber and a second tubularsleeve section disposed about the actuator pin for forming a bearingsleeve to receive the actuator pin. The damping member resides in thedamping chamber in a manner to reduce or dampen pressure oscillationsresulting from electrical, mechanical and/or hydraulic noise in thecontrolled fluid system or circuit, thereby improving valve responsestability.

Pursuant to another embodiment of the present invention, the solenoidfluid control valve includes a solenoid coil, an armature movable inresponse to electrical current applied to the solenoid coil, a valvemember for controlling fluid flow to a fluid passage, an actuator pindisposed between the armature and the valve member for moving the valvemember in response to armature movement, and further features that theactuator pin includes a sleeve fixedly attached thereto so as to movetherewith and having an annular sealing edge to engage a flat, fixedexhaust seat insert downstream of the valve member to close off fluidflow to an exhaust port when the armature is at an end position of itsstroke where the valve member is unseated a maximum distance from itsseat by the actuator pin. The sealing edge can be formed by chamferingor radiusing an end of the sleeve. The exhaust sealing edge/exhaust seatinsert reduce leakage of fluid to the exhaust port when the valve memberis unseated a maximum distance from its seat.

Pursuant to still another embodiment of the invention, the solenoidfluid control valve includes a solenoid coil, an armature movable inresponse to electrical current applied to the solenoid coil, a valvemember for controlling fluid flow to a fluid passage, an actuator pindisposed between the armature and the valve member for moving the valvemember in response to armature movement, and the further feature that aparticle gettering magnet is disposed inside a fluid-containing housingof the fluid control valve to capture ferrous particles in the fluid. Inan embodiment of the invention, the particle gettering magnet isdisposed about a tubular bearing sleeve receiving the actuator pin so asto capture ferrous particles that may be present in the fluid proximatethe bearing sleeve.

Pursuant to still a further embodiment of the present invention, thesolenoid operated fluid control valve includes a solenoid coil, anarmature movable in response to electrical current applied to thesolenoid coil, a valve member for controlling fluid flow to a fluidpassage, an actuator pin disposed between the armature and the valvemember for moving the valve member in response to armature movement, andthe further feature that a flow diverter is disposed in the fluidpassage adjacent the valve member for imparting turbulent flow to fluidin the fluid passage to improve valve response stability at low controlpressure. In an embodiment of the invention, the flow diverter isdisposed in the fluid passage to support an end region of the actuatorpin adjacent the valve member. An opposite end region of the actuatorpin is supported by a bearing sleeve proximate the armature such that aninner end of the armature can be supported by hydrodynamic fluidpressure to reduce hysteresis losses in operation of the fluid controlvalve.

Pursuant to still a further embodiment of the present invention, thesolenoid operated fluid control valve includes a solenoid coil, anarmature movable in response to electrical current applied to thesolenoid coil and the further feature that a tubular solenoid coilbobbin support sleeve or liner is disposed between the coil bobbin andthe armature to maintain valve response stability over time attemperatures to which the valve components are exposed in service. Thesleeve or liner completes a solid axial stacking path from a permanentmagnet to a flux washer in a manner to reduce possible thermal drift ofthe permanent magnet that could affect valve response over time. A spaceor gap preferably also is provided between an end of the coil bobbin andthe adjacent flux washer to help avoid harmful thermal drift of thepermanent magnet.

The invention envisions a solenoid operated fluid control valve havingone or more of the above features. Moreover, the invention envisions inother embodiments a proportional variable force solenoid operated fluidcontrol valve of the type having a permanent magnet disposed in asolenoid housing of the control valve housing about an outer end regionof the armature to provide a permanent magnetic field with which thevariable electromagnetic field of the solenoid coil interacts to move aspring-biased armature in a manner proportional to the electricalcurrent supplied to the solenoid coil and further having one or more ofthe above features.

The foregoing and other features and advantages of the invention willbecome apparent from the following more detailed description taken withthe accompanying following drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a longitudinal cross-section view of a proportional variableforce solenoid fluid control valve illustrating certain embodiments ofthe present invention showing the ball valve member in a full openposition.

FIG. 2 is longitudinal cross-section view of the proportional variableforce solenoid fluid control valve of FIG. 1 taken 90 degrees to theplane of FIG. 1 showing the ball valve member in a closed position.

FIG. 3 is an enlarged view of the ball valve and flow diverter.

FIGS. 3A and 3B are enlarged partial sectional views of differentchamfered sealing edges formed on the end of a sleeve.

FIG. 3C is an enlarged partial sectional view of a radiused sealing edgeformed on the sleeve. FIG. 4 is an end elevation of the flow diverter.

FIG. 5 is a graph of control pressure and total flow versus solenoidelectrical current when the fluid control valve is operated in aproportional manner where control pressure increases in proportion tocoil current.

FIG. 6 is a graph of control pressure and total flow versus solenoidelectrical current when the fluid control valve is operated in aninversely proportional manner where control pressure decreases inproportion to coil current.

FIG. 7 is a partial longitudinal cross-section view of a proportionalvariable force solenoid fluid control valve illustrating anotherembodiment of the present invention having a sleeve or liner to providea solid stacking path.

DESCRIPTION OF THE INVENTION

Features and embodiments of the invention will be described below inconnection with a particular proportional variable force solenoid fluidcontrol valve of the type having a permanent magnet disposed in asolenoid section of the control valve housing to provide a permanentmagnetic field with which the variable electromagnetic field of thesolenoid coil interacts to move a spring-biased armature in a mannerproportional to the electrical current supplied to the solenoid coil.Proportional variable force solenoid fluid control valves of this typeare described in U.S. Pat. Nos. 4,988,074; 5,611,370; 5,984,259;5,996,628; and 6,179,268. However, the invention is not limited topractice with such proportional variable force solenoid fluid controlvalves in that the invention can be practiced with other types ofsolenoid operated fluid control valves for controlling fluid pressure ina fluid system in response to electrical current applied to a solenoid.

Referring to FIGS. 1-2, an illustrative proportional variable forcesolenoid fluid control valve 10 includes a valve or nozzle housing 12having a fluid valve member 14 and associated components therein and asolenoid housing 16 having a solenoid 18 disposed therein in a manner toprovide a fluid control valve of the general types described in theabove U.S. Pat. Nos. 4,988,074; 5,611,370; 5,984,259; 5,996,628; and6,179,268, of common assignee herewith, the teachings of which areincorporated herein by reference. The valve housing 12 can be made ofaluminum, while the solenoid housing 16 can comprise steel or otherferromagnetic material pursuant to U.S. Pat. No. 4,988,074. The valvehousing 12 and solenoid housing 16 are joined together at radial annularsolenoid housing flanges and radial annular valve housing flanges asshown in the above U.S. Pat. Nos. 4,988,074; 5,611,370; etc. The valvehousing 12 and the solenoid housing 16 alternatively can be formed as asingle, common housing, pursuant to Najmolhoda U.S. Pat. No. 5,611,370with the common housing made of a substantially non-magnetic materialwith little or no magnetic permeability.

A material particularly suited for such a common or single housingcomprises aluminum and its alloys or thermoplastic formed by casting orinjection molding to required housing configuration. The common housingwill include a housing section or region for enclosing the solenoid 18and a nozzle housing section or region for enclosing the valve member 14and associated valve components.

Referring to FIGS. 1-2, the solenoid 18 is disposed in the solenoidhousing 16 (or solenoid housing section of the common housingembodiment) and includes an electromagnetic solenoid coil wound about amolded plastic bobbin 21 which has a cylindrically shaped bore hole 21athrough the longitudinal axis thereof. The bobbin 21 is made of glassfilled thermoplastic or any other suitable material. An axiallyelongated armature 22 formed of a ferromagnetic material (e.g.magnetically permeable steel) is suspended within the bore hole 21a by athin low spring rate spring 24 mounted at a rear, outermost end 22a ofthe armature: A plastic electrical connector body 52 is mounted on thebobbin 21 by snap fit, mechanical interlock, heat staking, or otherfastening method. The electrical connector body 52 includes electricalterminal contact pins 54a, 54b connected to the wires of theelectromagnetic coil 20 for receiving an electrical current signal froma variable current source (not shown). Electrical contacts are shown inthe aforementioned U.S. Pat. No. 4,988,074. The contact pins 54 a, 54 bin turn are connected to respective electrical terminals 55 a, 55 b forconnecting the fluid control valve to a source of electrical currentsignals. For purposes of illustration and not limitation, the terminals55 a, 55 b can be connected to a conventional electronic transmissioncontrol module (not shown) of a motor vehicle by a lead frame or wiringharness when the fluid control valve is used to control a vehicletransmission. In this application, the valve housing 12 of the fluidcontrol valve is received in a bore B of a transmission fluid manifold Mwith seals S1, S2 engaging the transmission manifold and separating thefluid supply circuit, the fluid control circuit, and the fluid exhaustcircuit from one another.

For purposes of illustration and not limitation, the plate spring 24 isof the type described in the aforementioned U.S. Pat. No. 4,988,074 andis formed from very thin non-magnetic austenitic stainless steel, suchas full hard austenitic stainless steel, which provides a very low ratespring for the spring configuration shown in FIG. 5 of theaforementioned '074 patent. The inner periphery of the plate spring 24is mounted between a steel annular retainer member 19 and the outer endof armature 22. The outer periphery of the plate spring 24 is mountedbetween an end surface of bobbin 21 and the axially magnetized permanentmagnet ring 34 so as to suspend the armature 22 for free axiallongitudinal movement within the bobbin 21. The bobbin 21 includes aheat-staked flange 21 f that holds the permanent magnet ring inposition.

The axially magnetized permanent magnet ring 34 is disposed in thesolenoid housing at the outer end 22 a of the armature 22 axiallyrearward of the solenoid coil 20 and about at least a portion of thearmature end. For purposes of illustration and not limitation, thepermanent magnet ring 34 is formed of rare earth permanent magnetmaterial, such as Sm—Co or Nd₂Fe₁₄B, permitting use of a reduced sizemagnet that results in a compact solenoid. The permanent magnet ring 34produces a permanent magnetic field that substantially saturates thearmature 22 even in the absence of electrical current to the coil 20.Thus, a relatively smaller magnetic field is required to move thearmature 22 between the axial end position of the armature stroke shownin FIG. 1 where valve member 14 is unseated relative to its valve seatand an axial position to the left in FIG. 2 where valve member 14 isseated on its valve seat. In the position of FIG. 1, the valve member 14is open to allow communication between supply port 72 and the controlport 73 as regulated by an exhaust valve member as described below. Inthe position of FIG. 2, the valve member 14 is closed on its seat tointerrupt communication between supply port 72 and the control port 73.

The permanent magnet ring 34 also is clamped against the bobbin by anend closure 45 held on the solenoid housing 16 by housing flange 16 gcrimped over the end closure. The end closure 45 includes a deformableend cap 46 that engages an outer end of a coil compression spring 42(spring biasing means). The end closure 46 is held on the end closure 45by being trap fit or captured by housing 16. The spring 42 is trappedbetween the armature outer end 22 a and the deformable end cap 46. Thecentral region of the deformable end cap 46 is deformed after assemblyof the valve to adjust valve response to solenoid current as describedin U.S. Pat. No. 5,996,628, the teachings of which are incorporatedherein by reference. The armature 22 is biased by coil spring 42 toplace the valve member 14 in the open position off its seat when thesolenoid coil 20 is deenergized as described below.

The opposite front, inner end 22b of the armature is unsupported, exceptby hydrodynamic fluid pressure in the bore of the bobbin 21. Support ofthe armature 22 in this manner reduces friction effects on armaturemovement and thus hysteresis losses in operation of the fluid controlvalve. The flux washer W may be provided adjacent the bobbin 21 pursuantto aforementioned U.S. Pat. No. 4,988,074, incorporated herein byreference, to concentrate electromagnetic flux at the inner end 22 b ofthe armature 22.

The inner end 22 b of the armature includes a cylindrical armature pin22 p made of carbon steel and is fastened (e.g. press fit) thereto so asto move with the armature 22. The armature pin 22 p extends along thecentral longitudinal axis of the fluid control valve 10 and protrudesslightly beyond the inner end of the armature 22.

As shown in FIGS. 1-2, a fluid damping member 25 is associated with theinner end of the armature 22 so as to move with the armature. Thedamping member 25 can be formed integral with the inner end 22 b of thearmature 22 as shown, or can be connected or abutted thereto so as tomove with the armature 22 if the damping member is a separate element asdescribed in U.S. Pat. No. 5,984,259.

Pursuant to an embodiment of the invention, the damping member 25resides in a fluid damping chamber 27 defined by an inner wall 23 w oftubular actuator pin support body 23 disposed in the fluid-containingvalve or nozzle housing valve 12, or valve or nozzle section of a commonhousing. The tubular actuator pin support body 23 is described in moredetail below. The damping member 25 is disposed in the damping chamber27 in a manner to reduce or dampen pressure oscillations resulting fromelectrical, mechanical and/or hydraulic noise in the controlled fluidsystem or circuit as described in U.S. Pat. No. 5,984,259, therebyimproving valve response stability. In an electronically controlledautomobile transmission application, electromechanical noise in thecontrolled system or circuit can originate in the transmission controlmodule (e.g. a chopped pulse width control signal) and oscillations ofthe clutch or shift valves in the transmission body and produce fluidpressure oscillations and a non-linear valve response.

For purposes of illustration and not limitation, the armature dampingmember 25 has a cylindrical outer periphery adjacent the innercylindrical wall 23 w. The cross-sectional area of the damping member 25and the clearance between the cylindrical outer periphery of the dampingmember 25 and the cooperating wall 23 w are selected effective to reduceor damp pressure oscillations resulting from noise in the controlledfluid system or circuit, which pressure oscillations can result innon-linear valve response performance as described in U.S. Pat. No.5,984,259. An exemplary cross-sectional area of the damping member 25(cross-sectional area calculated using the outer diameter of dampingmember 25) can be 0.039 inch² (0.54 inch outer diameter of dampingmember). For this exemplary cross-sectional area of the damping member25, an exemplary radial clearance of approximately 0.005 inch can beprovided between the outer periphery of the damping member 25 and theinner wall 23 w for the proportional variable force solenoid fluidcontrol valve shown in FIGS. 1-2 adapted for use in a hydraulicautomatic transmission application for controlling a gear shiftinghydraulic circuit, although the invention is not limited in this regard.In effect, the damping chamber 27 and the damping member 25 provide atrapped volume of fluid comprising predominantly hydraulic fluid whichmust be moved through the restricted clearance area between the outerperiphery of the damping member 25 and the inner wall 23 w and in doingso reduces or damps pressure oscillations resulting from electrical,mechanical, and/or hydraulic noise in the controlled fluid system orcircuit.

As mentioned, the armature 22 is supported by spring plate 24 and byhydrodynamic fluid pressure in the bobbin 23 to reduce hysteresis lossesin operation of the fluid control valve 10.

Pursuant to an embodiment of the invention, a non-magnetically permeableactuator pin 31 is supported independently of the armature 22 in thevalve or nozzle housing 12, or valve section of a common housing. Forpurposes of illustration and not limitation, the actuator pin can bemade of austenitic stainless steel or other material having little or nomagnetic permeable compared to the steel or iron armature to this end.The actuator pin 31 and armature 22 are coaxial so to move along acommon longitudinal axis of the fluid control valve 10.

The actuating pin 31 is independently supported from the armature 22 byactuator pin support body 23. In particular, the support body 23includes a relatively large diameter, axially extending tubularcup-shaped section 23a that forms the damping chamber 27 therein and arelatively smaller diameter, axially extending tubular section 23 b thatforms a bearing tube or sleeve that is coaxial with the longitudinalaxis and that receives a cylindrical end 31 a of the actuator pin 31 ina precision bearing fit. The tubular cup-shaped section 23 a includesinner wall 23 w that coacts with the damping member 25 as describedabove and an end wall 23 e that abuts flux washer W. The actuator pinsupport body 23 is held in position in the valve or nozzle housing 12,or section of the common housing, by being trap fit (captured) therein.For purposes of illustration and not limitation, the actuator pinsupport body 23 is made of machine grade or form grade half hard brassmaterial.

The other opposite cylindrical end 31 b of the actuator pin 31 issupported by a flow diverter 110 residing adjacent valve member 14 aswill described further below. The actuator in 31 thereby isindependently supported for movement along the longitudinal axis duringoperation of the fluid control valve 10.

Pursuant to another embodiment of the invention, a particle getteringmagnet 33 is disposed inside fluid-containing valve or nozzle section12, or valve section of a common housing, to capture ferrous particlesin the fluid inside the fluid control valve 10. In FIGS. 1-2, theparticle gettering magnet 33 is shown as a magnet ring disposed in thevalve housing section 12 about the tubular bearing tube or sleeve 23 breceiving the actuator pin 31 so as to capture ferrous particles thatmay be present in the fluid proximate the bearing tube or sleeve. Themagnet ring is trap fit (captured), light interference press fit orotherwise secured in a bore of the valve or nozzle housing 12 to hold itin position about the bearing sleeve 23 b. For purposes of illustrationand not limitation, the particle gettering magnet can comprise apermanent magnet ring, such as Nd₂Fe₁₄B or any type of magnet thatattracts ferrous particles in the fluid to remove them from the fluidand thus from entering the bearing sleeve 23 b. A second particlegathering magnet 33′ can be disposed in the supply passage of thetransmission manifold M to which the fluid control valve is communicatedto remove ferrous particles from the supply fluid before they enter thevalve or nozzle housing 12 via the supply port 72.

The valve or nozzle housing 12 is disposed in a bore or chamber in castaluminum transmission housing manifold M, or other fluid control system.Outer O-ring seals S1, S2 on the valve housing 12 seal on thetransmission housing manifold and separate the hydraulic fluid supplyand control lines or conduits (not shown) of the transmission hydrauliccircuit.

The valve or nozzle housing 12 includes at least one pressurizedhydraulic fluid supply or inlet port 72, at least one control port 73,and at least one exhaust port 74. The supply or inlet port 72communicates to an inner fluid chamber 12 c of the valve or nozzlehousing 12. To this end, annular supply port 72 is provided andcommunicates to one or more side supply passages 12 b, which in turncommunicate to the inner fluid chamber 12 c.

The outer end of the fluid chamber 12 c is closed by a threaded closureplug 15 threadably received in an end bore of the valve or nozzlehousing 12. A valve member 14, which is illustrated as a ball valve, isconfined for axial movement in the fluid chamber 12 c between theclosure plug 15 and a valve seat 12 s.

Tubular fluid filter screen assembly F can be provided on the valve ornozzle housing 12 at the supply port 72 as well as the control port 73as shown in U.S. Pat. Nos. 5,984,259 and 6,179,268, the teachings ofwhich are incorporated herein by reference, to help capture harmful dirtand debris particles that may be present in the fluid.

The inner fluid chamber 12 c communicates to valve seat 12 s such thatthe ball valve 14 controls fluid flow through orifice 12 o of the valveseat 12 s to axially extending cylindrical fluid passage 12 p locateddownstream of the ball valve 14 in valve or nozzle housing 12, FIG. 3.The fluid passage 12 p communicates via intermediate chamber or passage12 k to side or lateral passages 12 m, 12 n which communicate to thecontrol port 73, FIG. 2. The fluid passage 12 k thus is disposed betweenthe supply port and the control port 73 in a fluid flow sense. The fluidpassage 12 k also is disposed between the supply port 72 and the exhaustport 74 in a fluid flow sense. In the illustrative embodiment shown inFIGS. 1-3, the fluid passage 12 k functions as a pressure regulatingpassage.

The actuator pin 31 extends from the bearing tube or sleeve 23 b throughan exhaust chamber 12 e of the valve or nozzle housing 12, through anexhaust orifice 100 a of an exhaust seat insert 100, through passage 122a of a flow diverter 110, FIG. 4, through passages 12 k, 12 p, andthrough the orifice 12 o of the valve seat 12 s where the outermost endof the actuator pin contacts the ball valve 14 so that the position ofthe ball valve 14 relative to its seat 12 s is controlled by movement ofthe armature 22 in response and in proportion to the current level ofthe electrical current signals input to the solenoid coil 20. The innerfluid chamber 12 c communicates the fluid supply port 72 and fluidcontrol port 73 in flow relation as permitted by ball valve 14. Theexhaust orifice 100 a of the exhaust seat insert 100 communicates thefluid passage 12 p, 12 k to the exhaust chamber 12 e and thus theexhaust port 76 leading to a conventional sump or return tank (notshown) of the fluid control system. The exhaust seat insert 100 is heldin position by retainer ring 77.

The actuating pin 31 includes cylindrical end region 31 a received inthe bearing tube or sleeve 23 b, an opposite cylindrical end 31 b thatengages the ball valve 14, and a cylindrical tubular sleeve 31 c pressfit or otherwise fixedly attached on the enlarged region of the actuatorpin disposed intermediate the ends 31 a, 31 b. The sleeve 31 c includesan annular sealing edge 31 s, FIG. 3, on an end thereof so as to engagethe flat seating (backface) surface 100 b of the exhaust seat insert 100downstream of the valve member 14 to close off fluid flow to the exhaustport 74 when the valve member 14 is unseated a maximum distance from itsseat 12 s by the actuator pin as shown in FIG. 1. The flat seatingsurface 100 b preferably extends perpendicular to the longitudinal axisof the actuator pin. The sealing edge 31 s can be formed by chamferingthe end of the sleeve 31 c as shown in FIG. 3A or FIG. 3B, by providinga full radius on the end of sleeve 31 c as shown in FIG. 3C, or by anyother technique to provide a sealing edge 31 s. For purposes ofillustration and not limitation, a 2 degree or other chamfer can beprovided on the end of sleeve 31 c in FIGS. 3A or FIG. 3B to form thesealing edge. The exhaust sealing edge 31 s/exhaust seat insert surface100 b thereby reduce leakage of fluid to the exhaust port 74 when thevalve member is unseated a maximum distance from its seat.

As mentioned above, the actuator pin 31 extends through a passage 122 aof the fluid diverter 110, which is located in passage 12 k spaceddownstream of and in communication with fluid passage 12 p so that fluidfrom passage 12 p impinges on the side of the flow diverter. The flowdiverter 110 imparts turbulent flow to fluid from the fluid passage 12 pto counter possible changes in fluid viscosity (and higher fluidvelocity) resulting from higher fluid temperatures during valveoperation and/or effects of possible negative fluid pressures at lowcontrol pressures due fluid being exhausted at the exhaust port 74. Theturbulence created by the flow diverter improves valve responsestability by eliminating negative pressure (venturi effect) due tolaminar flow to the exhaust.

The flow diverter 110 is shown in FIG. 4 to include a central hub 122having an axial passage 122 a through which end 31 b of actuator pin 31extends. The flow diverter also includes multiple lobes or arms 124 thatextend from the hub and are spaced apart at the hub periphery to providefluid flow channels 124 c communicated to the exhaust orifice 100 a. Thefluid flow channels 124 c provide a fluid flow path for fluid from thevalve seat orifice 12 o to the exhaust orifice 100 a. The flow diverteris positioned in chamber 12 k by posts 127 being received in recessedpockets in the nozzle housing 12, FIG. 4. The arms 124 have axiallyenlarged ends that abut on the facing side of the insert 100, FIG. 3.The flow diverter 110 includes one or more (a pair being shown in FIG.3) of cylindrical standoff bosses 129 molded on the flow diverter sidefacing the passage 12 p to maintain a flow path for fluid from passage12 p to passages 12 m, 12 n. For purposes of illustration and notlimitation, the flow diverter 110 can be made of molded thermoplastic orother material.

FIG. 1 shows operation of the fluid control valve with no electricalcurrent signal applied to the solenoid coil 20. The armature 22 andactuator pin 31 are moved in unison to the right in FIG. 1 by the biasof coil compression spring 42 toward a first armature end position ofits stroke where the ball valve 14 is moved by actuator pin 31 to be ata maximum distance from its valve seat 120 (i.e. ball full open positionrelative to its seat). The distance is equal to the distance of the seat12 s to the sealed surface (backface) 100 b of exhaust seat 100 plus thedesired amount of ball travel. In this first position, the supply port72 is fully communicated to control port 73, and the exhaust sealingedge 31 s is sealed against the sealed surface (backface) 100 b. Thisarmature position provides the maximum fluid flow to the fluid passage12 p and thus to control ports 73, while there is little or no leakageof the fluid to the exhaust port 74 by virtue of the sealing edge 31 sbeing sealed against the sealed surface (backface) 100 b.

On the other hand, in operation of the fluid control valve of FIG. 2with electrical current signal applied to the solenoid coil 20, thearmature 22 is moved by interaction of the electromagnetic field of thesolenoid coil and the permanent magnetic field toward the left in FIG. 1against the bias of the coil spring 42 toward the other (second) endarmature position of its stroke where the ball valve 14 s is positionedat the closed position on its valve seat 12 s by fluid pressure in fluidchamber 12 c. The actuating pin 31 follows movement of the armature 22to the left in FIG. 1 as a result of fluid pressure in the fluid chamber12 c.

Movement of the armature 22 between these first and second end positionsof its stroke can be controlled in a linear proportional manner independence on electrical current provided to the solenoid coil. Forexample, in a proportional mode of operation with the ball valve 14initially closed on seat 12 s, electrical current is supplied to thecoil 20 via the contacts 54 a, 54 b in a manner to create anelectromagnetic field which cooperates with the permanent field andforce of compression spring 42, which are opposed by force of platespring 24 and fluid pressure on ball valve 14, to move the ball valve 14away from its seat 12 s in a linear proportional manner to the currentlevel applied to coil 20 so as to, in turn, vary control pressure in alinear proportional manner where the control pressure increases withincreasing solenoid current. For purposes of illustration and notlimitation, FIG. 5 shows the control pressure and total flow versuselectrical current to the solenoid in the proportional mode of operationwhere the control pressure increases with increasing solenoid current.

A inversely proportional mode of operation with the ball valve 14initially open can also be provided by the fluid control valve shown byeither reversing the current flow direction through the solenoid coil 20or reversing the direction of polarization of the permanent magnet 34 sothat energization of the solenoid coil with electrical current moves theball valve 14 from the open position to the closed position on the valveseat 12 in a linear proportional manner so as to, in turn, vary controlpressure in an inverse linear proportional manner where the controlpressure decreases with increasing solenoid current. For purposes ofillustration and not limitation, FIG. 6 shows the control Pressure andtotal flow versus electrical current to the solenoid in the inverselyproportional mode of operation where the control pressure decreases withincreasing solenoid current.

A solenoid operated fluid control valve pursuant to another embodimentof the invention is illustrated in FIG. 7 where like features bear likereference numerals. The solenoid operated fluid control valve differsfrom the embodiment of FIGS. 1-2 in having a further feature comprisinga tubular (e.g. generally cylindrical) solenoid coil bobbin supportsleeve or liner 150 disposed between the molded plastic coil bobbin 21and the armature 22 to maintain valve response stability over time atservice temperatures to which the valve components are exposed inservice. Other valve components of FIG. 7 are similar to those describedabove in connection with FIGS. 1-2. The sleeve or liner 150 is disposedin trap or slight interference fit in the bore of bobbin 21. Inparticular, in the embodiment of FIGS. 1-2, the coil bobbin 21 mayexperience thermal drift due to thermoplastic creep, thermal dimensionalchange or the like, over time at service temperatures to which the valvemay be exposed. In use in a vehicle transmission module, servicetemperatures may range from −40 degrees C. to 150 degrees C. Suchthermal drift of the bobbin 21 may cause the permanent magnet positionto drift or be displaced in an axial direction to an extent that valveresponse is altered over time. The sleeve or liner 150 is disposed tocomplete a solid axial stacking path, where certain valve components areaxially abutted from permanent magnet 34 to a flux washer W in a mannerto reduce possibility of axial drift of the permanent magnet that couldaffect valve response over time. For example, one end of the sleeve orliner 150 axially abuts the flux washer W while the other enlarged end,together with the permanent magnet 34, axially abuts and traps the outerperiphery of the plate spring 24. The sleeve or liner 150 can comprisebrass or any other appropriate metallic material or other material. Anaxial space or gap 152 is provided between the axial end of the coilbobbin 21 and the adjacent flux washer W to accommodate possible thermaldrift of the bobbin assembly over time at the service temperatures ofthe valve, avoiding harmful drift of the permanent magnet 34.

Although certain preferred embodiments of the proportional variableforce solenoid valve and fluid control device for an electronictransmission of the invention have been shown and described in detail,it should be understood that variations or modifications may be madewithout departing from the spirit or scope of the present invention.

1.-10. (canceled)
 11. Solenoid fluid control valve, comprising asolenoid coil, an armature movable in response to electrical currentapplied to the solenoid coil, a valve member for controlling fluid flowto a fluid passage, an actuator pin disposed between the armature andthe valve member for moving the valve member in response to armaturemovement, and a particle gettering magnet disposed inside afluid-containing housing of the fluid control valve to capture ferrousparticles in the fluid.
 12. The fluid control valve of claim 11 whereinthe particle gettering magnet is disposed inside the housing about atubular bearing sleeve receiving the actuator pin.
 13. The fluid controlvalve of claim 11 wherein the particle gettering magnet comprises aring-shaped magnet disposed about the tubular bearing sleeve.
 14. Thefluid control valve of claim 11 further including a permanent magnetdisposed about an outer armature end.
 15. The fluid control valve ofclaim 11 further a particle gettering magnet in a fluid supply passageof a transmission manifold to which the fluid control valve iscommunicated. 16-27. (canceled)